TWM496698U - Mounting base for motor/generator - Google Patents

Abstract

A motor or generator assembly including a motor or generator machine and mounting structure supporting the machine on an appliance is provided. The machine presents an axially extending, radially outermost circumferential face and a pair of axially spaced apart, radially projecting axial margins. The mounting structure includes a pair of at least substantially radially extending plates and a base configured for connection to the appliance. The plates extend at least in part adjacent respective ones of the axial margins and at least in part define a machine-receiving space therebetween. The machine is mounted on the brackets so as to be positioned at least in part in the machine-receiving space. The base is positioned at least substantially radially outside the circumferential face of the machine and presents a pair of axially spaced apart side faces, with each of the plates being secured against a respective one of the side faces.

Description

Mounting base for motor/generator

This creation is generally directed to an electric motor or generator assembly suitable for use in an appliance. More specifically, the present invention relates to a mounting base for securing an electric motor or generator assembly in an appliance.

One of ordinary skill will appreciate that electric motors or generators are used in a variety of applications including, but not limited to, appliances such as exercise bikes, rowing machines, ceiling fans, dishwashers, and washing machines, and vehicles such as automobiles and golf balls. car). In a fitness bicycle, for example, a generator can be provided. The generator is driven by the user's pedal and supplies power to a display that displays parameters such as the user's simulated speed or distance, the amount of time the pedal is being used, and the like.

A conventional mounting structure for supporting a motor or generator may include a bracket or plate that supports the motor or generator. Time-consuming bracket alignment and interstitial space between the rotor and the stator are often necessary during the installation of the motor or generator on the appliance. Accordingly, a need exists for an accurately formed mounting configuration that can be formed in an efficient and cost effective manner and that minimizes the mounting envelope required for the motor or generator assembly as a whole.

According to one aspect of the present invention, a motor or generator assembly for use with an appliance is provided. The motor or generator assembly includes a motor or generator and supports the machine One of the mounting structures on the appliance. The machine includes a rotor that is rotatable about an axis, and a stator. The machine presents an axially extending radially outermost circumferential surface. The machine presents a pair of axially spaced apart axial edges, each of the axial edges extending generally radially inward from the circumferential surface. The mounting structure includes a pair of plates that extend at least substantially radially and a base. The panels at least partially define a machine storage space therebetween. The machine is mounted to the brackets for at least partial positioning in the machine storage space. The plates extend at least partially adjacent to each of the axial edges. The base is positioned at least substantially radially outward of the circumferential surface of the machine. The base is configured for connection to the appliance. The base presents a pair of axially spaced sides, wherein each of the plates is fastened against each of the ones of the sides.

This [new content] is provided to introduce a choice of concepts in a simplified form. These concepts are further described below in the detailed description of the preferred embodiments. This [new content] is not intended to identify key features or essential features of the claimed subject matter, and is not intended to limit the scope of the claimed subject matter.

Various other aspects and advantages of the present invention will be apparent from the description of the appended claims.

10‧‧‧ Appliances

12‧‧‧Motor or generator assembly

14‧‧‧Motor or generator assembly

16‧‧‧Support assembly

18‧‧‧Installation structure

20‧‧‧ Stator

20a‧‧ core

20b‧‧‧Wiring

22‧‧‧Rotor

24‧‧‧ outermost machine surface

26‧‧‧Axial machine edge

28‧‧‧Axial machine edge

30‧‧‧Leader

32‧‧‧End cover

34‧‧‧Rotor cladding

36‧‧·wheels

38‧‧‧ magnet

40‧‧‧Inertial ring

42‧‧‧Base plate

44‧‧‧ side wall

46‧‧‧ innermost

48‧‧‧ outermost

50‧‧‧Wheel area

52‧‧‧Main area

54‧‧‧Sloping transition zone

56‧‧‧ Ventilation opening

58‧‧‧Stepped area

60‧‧‧welding line

62‧‧‧welding line

64‧‧‧ shaft parts

66‧‧‧Drive end bearing

68‧‧·Wheel bearing

70‧‧‧ one-way bearing

72‧‧‧opposite bearings

74‧‧‧Driver

76‧‧‧ opposite end

78‧‧‧ Notch

80‧‧‧ Middle section

82‧‧‧ bearing holes

84‧‧‧ bearing holes

86‧‧‧ bearing holes

88‧‧‧ bearing holes

90‧‧‧ buckle

92‧‧‧ buckle

94‧‧‧ buckle

96‧‧‧ buckle

98‧‧‧ Groove

100‧‧‧ Groove

102‧‧‧ Groove

104‧‧‧ Groove

105‧‧‧Washers

106‧‧‧Axis support

108‧‧‧End cover hub

110‧‧‧ board/bracket

112‧‧‧ board/bracket

114‧‧‧Axis support fasteners

116‧‧‧End cap fasteners

118‧‧‧Axis support flange

120‧‧‧ shoulder

122‧‧‧End cap hub flange

124‧‧‧Spring washers

126‧‧‧ spacers

128‧‧‧ drive end face

130‧‧‧opposite end faces

132‧‧‧ bearing ball

134‧‧‧ bearing ball

136‧‧‧ bearing ball

138‧‧‧ struts

140‧‧‧ Bearing Balls

142‧‧‧Internal seat

144‧‧‧External seat

146‧‧‧Internal seat contact surface

148‧‧‧External race contact surface

150‧‧‧Internal bracing contact surface

152‧‧‧External bracing contact surface

154‧‧‧Axis key

156‧‧‧Rotor key

158‧‧‧ shaft recess

160‧‧‧Internal seat notch

162‧‧‧Wheel recess

164‧‧‧External seat notch

166‧‧‧Base

168‧‧‧machine storage space

170‧‧‧ gap or space

172‧‧‧ gap or space

174‧‧‧ side

176‧‧‧ side

178‧‧‧ split draft face

180‧‧‧ bottom

182‧‧‧Base flange

184‧‧‧Base flange section

186‧‧‧Base flange section

188‧‧‧Base fastener storage slot

190‧‧‧Part 1

192‧‧‧Part II

194‧‧‧ front area

196‧‧‧After the region

198‧‧‧Drawing line/splitting line

200‧‧‧ concave curved area

202‧‧‧ radial clearance

204‧‧‧Adjacent areas

206‧‧‧Adjacent areas

208‧‧‧Axial internal surface

210‧‧‧Axial internal surface

212‧‧‧Connection location

214‧‧‧ fastener storage hole

214a‧‧‧The first collection of fastener storage holes

214b‧‧‧Second collection of fastener storage holes

216‧‧‧ plate hole

216a‧‧‧The first group of plate holes

216b‧‧‧The second group of plate holes

218‧‧‧ board fasteners

1 is a front perspective view of an appliance and an electric motor or generator assembly configured for use with the appliance; FIG. 2 is a rear perspective view of the electric motor or generator assembly of FIG. 1; FIG. Figure 2 is an enlarged top rear perspective view of the base of the assembly of Figure 2; Figure 4 is a bottom front perspective view of the base of Figure 3; Figure 5 is a plan view of the base of Figures 3 and 4; Figure 6 is a side view of the base of Figures 3 to 5; Figure 7 is a rear view of the base of Figures 3 to 6; Figure 8 is along Figure 6. Figure 3 is a cross-sectional view of the base of Figures 3 through 7 taken along line 8-8; Figure 9 is a cross-sectional view of the base of Figures 3 through 8 taken along line 9-9 of Figure 5; Figure 10 is a cross-sectional view of the susceptor of Figures 3 through 9 taken along line 10-10 of Figure 5; Figure 11 is a front perspective view of the rotor of the assembly of Figures 1 and 2, wherein a plurality of magnets are Figure 12 is an exploded front perspective view of the rotor of Figure 11, but with all of the magnets illustrated; Figure 13 is a side view of the rotor of Figure 12; Figure 14 is a view taken along line 14-14 of Figure 13 12 and FIG. 13 are cross-sectional views of the rotor; FIG. 15 is an exploded front perspective view of the assembly of FIGS. 1 and 2; and FIG. 16 is an exploded view of the shaft and bearing of the assembly of FIGS. 1, 2 and 15. Figure 17 is a front perspective view of the shaft member and bearing of Figure 16; Figure 18 is an incomplete front cross-sectional view of the assembly of Figures 1, 2, 15 and 16; Figure 19 is a front perspective view; Figure 2, Figure 2, Figure 16, and Figure 18 are partial cross-sectional front perspective views; Figure 20 is a locking group Of 15 to the diagonal struts 19 a cross-sectional side view of a clutch; and FIG. 21 is an oblique unlocked configuration in FIG. 20 cross sectional side view of the support of the clutch.

The drawings are not intended to limit the invention to the particular embodiments disclosed and described herein. The drawings are not necessarily to scale unless the

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

This creation is susceptible to implementation in many different forms. Although the drawings illustrate and describe certain preferred embodiments of the present invention, it is understood that this disclosure is by way of example only. It is not intended to limit the scope of the present invention to the particular disclosed embodiments.

Referring initially to Figure 1, an appliance 10 is provided. A motor or generator assembly 12 is provided for use with the appliance 10.

In a preferred embodiment, the motor or generator assembly 12 is a generator assembly, and the appliance 10 is an exercise device such as a gym or a home, such as a fitness bike, a multi-functional exercise machine, or an elliptical machine. The generator assembly 12 preferably provides resistance to the user as appropriate based on the particular appliance, and also provides power to operate the user interface and possibly other electronic devices (such as heart rate monitors). However, alternative generator powered devices may also be permitted including, but not limited to, rowing machines or non-fitness devices.

The motor or generator assembly 12 can also be permitted to be a motor assembly. In one embodiment, for example, the motor assembly can provide electrical power to an outdoor electric bicycle.

Preferably, the assembly 12 includes a motor or generator 14 that includes a support assembly 16. Assembly 12 further includes a mounting structure 18 for mounting machine 14 to appliance 10. Each of these components is discussed in more detail below.

Motor or generator

As best shown in Figures 1, 2 and 19, the motor or generator 14 includes a stator 20 and a rotor 22 that are rotatable about an axis. The rotor 22 is preferably an outer rotor that at least substantially defines the limits of the stator 20 such that the machine is an external rotor motor or an "inside-out" generator. More preferably, the rotor 22 completely defines the boundaries of the stator 20. However, according to some aspects of this creation In this case, the internal rotor can be used.

As will be discussed in more detail below and as best shown in Figures 1, 2 and 19 The machine 14 also preferably presents an axially extending radially outermost circumferential machine face 24 and a pair of radially extending axially spaced axial machine edges 26 and 28. Each of the axial edges 26 and 28 preferably extends radially inwardly from the circumferential surface 24 and at least substantially spans a region generally defined within the interior of the circumferential surface 24. In the illustrated embodiment, each of the axial edges 26 and 28 is substantially flat in the sense that it is defined by a structure that extends generally along a plane that is perpendicular to the axis of the rotor. However, the principles of the present invention are equally applicable to one or both of the axial edges having a contour such as a undulating or curved or sloping surface, whereby the axial edge is not an area that spans the boundary defined by the circumferential surface. The generally flat face.

Although the axial machine edges 26 and 28 may be at least partially structurally defined, continuous structural definition is not required in accordance with some aspects of the present teachings. Moreover, in accordance with some aspects of the present invention, it may be permitted to define axial edges with respect to the structure rather than defining the axial edges by the structure itself. Similarly, as illustrated, the circumferential faces need not be continuous or defined by the structure in an exclusive manner.

The stator 20 preferably includes a core 20a (partially shown) and a wiring 20b wound around the core 20a. Leads 30 are preferably provided to transfer power to or from the wiring 20a as needed for the selected appliance.

In a preferred embodiment, machine 14 includes an end cap 32 that is secured to stator 20 and supports the stator. In the illustrated embodiment, the end cap 32 cooperates with the stator 20 to at least substantially define the first axial machine edge 26.

As best shown in FIGS. 11-14, the rotor 22 preferably includes a rotor casing 34, a hub 36, a plurality of magnets 38, and an inertia ring 40. The cladding 34 preferably includes substantially A radially extending base plate 42 extends from the base plate 42 to present a radially innermost face 46 and a radially outermost face 48 of generally axially extending sidewalls 44. The base plate 42 is preferably circular and the side walls 44 are preferably cylindrical. However, alternative shapes are permissible.

Preferably, the base plate 42 includes a radially innermost hub region 50, a main region 52, and An inclined transition region 54 that is radially outside of the hub region 50 and extends between and interconnects the hub region 50 and the main region 52. However, more or fewer zones can be set without departing from the scope of the present creation.

Preferably, main zone 52 partially defines a second axial machine edge 28.

In a preferred embodiment, the base plate 42 includes a plurality of venting openings 56 extending therethrough. However, it is alternatively possible to provide only a single ventilation opening or even to provide a ventilation opening. Preferably, the venting openings are formed primarily through the main zone 52. The overlap into the transition zone 54 is also permitted due to placement in completely different and/or additional locations.

As best illustrated by FIG. 14, side wall 44 is preferably formed integrally with base plate 42. Optimally, the integrated stepped region 58 interconnects the base 166 and the side walls 44. However, alternative connecting members including non-integrated members may be permitted to be disposed between the sidewall and the base.

In a preferred embodiment, the cladding 34 is a stamped rotor cladding. However, depending on some aspects of the present creation, different methods of formation may be permitted. For example, the cladding may alternatively be cast or at least partially machined.

Preferably, the cladding 34 consists essentially of steel, but other materials may be used without departing from the scope of the present invention. For example, the cladding may consist essentially of cast iron or plastic or be formed from a metal alloy.

The hub 36 is preferably secured to the cladding 34 adjacent the hub region 50. Optimally, such as Most preferably shown in Figures 11, 14, and 18, the hub 36 is welded to the cladding 34 along the weld line 60 for rotation therewith. However, alternative fixed components fall within the scope of some aspects of the present creation. For example, the hub 36 can be secured to the cladding 34 with bolts.

Hub 36 preferably consists essentially of steel, but may permit the use of any one or more of a variety of materials.

In a preferred embodiment and as illustrated in FIG. 11 and other figures, the magnets 38 are disposed in an arcuate configuration along the sidewalls 44 of the rotor cladding 34 such that the rotor cladding 34 at least partially supports the magnets 38. Magnet 38 is preferably a permanent magnet and preferably comprises ferrite. However, any one or more of a variety of magnet types and/or materials may be used without departing from the scope of the present invention.

Preferably, the inertia ring 40 is configured to increase the rotational inertia of the rotor 22 about the axis by providing a mass that rotates about the axis with the rotor cladding 34. The configuration of the inertia ring 40 is varied to achieve a change in the rotational inertia of the rotor 22 as a whole without the complexity or other such complex methods associated with the design and manufacturing variations of the rotor cladding. For example, changes in the positioning, thickness, width, and/or material of the inertia ring 40 directly affect the overall rotational inertia of the rotor 22.

The inertia ring 40 is preferably not integrated with the rotor casing 34, but is fixed to the rotor casing 34 for rotation therewith. This fixing can be accomplished by any means known in the art (e.g., welding, screws, glue, adhesives, or combinations thereof), but soldering is preferred. Most preferably, the inertia ring 40 is welded to the sidewall 44 of the inertia cladding 34 along a generally axially extending weld line 62.

The inertia ring 40 preferably at least partially overlies at least one of a radially innermost surface 46 and a radially outermost surface 48 defined by the sidewalls 44. Most preferably, the inertia ring 40 at least partially overlaps the radially outermost portion 48 and thus presents the aforementioned axially extending radially outermost circumferential machine face 24.

In addition, the one of the faces 46 and/or 48 is adjacent to the inertia ring 40, The ring 40 preferably at least substantially overlaps or even completely overlaps the selected faces 46 and/or 48. As best shown in FIG. 14, for example, the inertia ring 40 completely overlies the radially outermost portion 48 and even extends axially beyond the radially outermost portion to suspend the stepped region 58.

As also best shown in Figure 14, the radial thickness of the sidewall 44 and the inertia ring 40 The radial thickness is preferably at least substantially similar. However, as noted above, the relative thickness can be varied relatively easily by changing the inertia ring design. The overall rotor inertia can be easily increased, for example, by providing a radially thicker inertia ring.

In a preferred embodiment, the inertia ring 40 is continuous on the circumference. However, according to some aspects of the present creation, it may be permitted to set a discontinuous loop. For example, the inertia ring can include a perforation or be formed from a plurality of segments that are spaced apart in an arcuate shape.

Preferably, the inertia ring 40 consists essentially of steel, but without departing from the creation In the case of some aspect categories, any one or more of a plurality of materials may be suitably used. As noted above, variations in the inertia ring material provide a relatively easy way to substantially change the rotational inertia of the rotor as a whole. For example, a cast iron inertia ring will increase rotational inertia relative to an aluminum inertia ring.

In a preferred embodiment, the inertia ring 40 and the rotor casing 34 are substantially It consists of materials that have substantially the same density. As noted above, for example, both the inertia ring 40 and the rotor casing 34 are preferably formed substantially of steel. However, depending on some aspects of the present creation, different densities may be permitted. The rotor cladding may be formed substantially of, for example, steel, and the inertia ring may consist essentially of iron.

It is also pointed out that according to some aspects of the creation, the inertia ring can be completely omitted, wherein The inertia of the rotor is at least substantially controlled by rotor cladding design or post production machining. For example, the rotor cladding can be a cast iron rotor cladding having sidewalls that initially have a large thickness that is machined to a desired outer diameter during processing.

Support assembly

As noted previously, the motor or generator assembly 12 preferably includes a motor or generator 14 that includes a support assembly 16. Assembly 12 further includes a mounting structure 18 for mounting machine 14 to appliance 10.

As best shown in Figures 18-19, the support assembly 16 preferably includes a shaft member 64 and a plurality of bearings 66, 68, 70 and 72.

As best shown in Figures 16 and 18, the shaft member 64 preferably presents a drive end 74 and an opposite end 76. In a preferred embodiment of the exercise bike of the appliance 10, the drive end is preferably interconnected directly or indirectly (e.g., via a gear or pulley system) to a pedal driven by a user such that the user's pedaling action drives the shaft member 64 rotation. However, in alternative embodiments, the drive and opposite end connections and functionality may vary depending on the particular appliance and application desired. It will be appreciated that even though the shaft ends 74 and 76 are depicted as being part of the machine 14, the ends 74 and 76 protrude from the axial machine edges 28 and 26, respectively.

Drive end 74 preferably includes a notch 78 that is configured for interconnection with a suitable structure to be driven. However, any type of interconnect structure may be permitted in addition to or as an alternative to the recess.

The shaft member 64 preferably includes an intermediate section 80 between the drive end 74 and the opposite end 76. As will be discussed in greater detail below, the intermediate section 80 preferably has a larger diameter than both the opposed end 76 and the drive end 74. Drive end 74 preferably has a larger diameter than opposed end 76.

The plurality of bearings 66, 68, 70 and 72 preferably include a drive end bearing 66, a hub bearing 68, a one-way bearing 70 and an opposite end bearing 72. However, depending on some aspects of the present creation, more or fewer bearings may be permitted to be placed.

Each of the bearings 66, 68, 70 and 72 preferably defines a corresponding bore 82, 84, 86 or 88. As will be discussed in more detail below, the holes 88 are preferably smaller than the holes 82, 84 and 86.

The drive end bearing 66 is preferably adjacent the drive end 74 to define the boundary of the intermediate section 80, while the opposed end bearing defines the boundary of the opposite end 76. Hub bearing 68 and one-way bearing 70 each preferably define a boundary of intermediate section 80 of shaft member 64 to position the intermediate section between drive end bearing 66 and opposed end bearing 72.

A plurality of retaining rings 90, 92, 94 and 96 are preferably provided to assist in axially securing the bearings 66, 68 and 70 along the shaft member 64. Preferably, the buckles 90, 92, 94 and 96 are snap rings, although other types of buckles may be suitably used.

In a preferred embodiment, a plurality of grooves 98, 100, 102 and 104 are formed in the intermediate section 80 of the shaft member 64. Each of the buckles 90, 92, 94, and 96 is preferably adapted to the counterpart of the grooves 98, 100, 102, and 104.

A gasket 105 can also be provided for additional fastening.

As best shown in Figures 18 and 19, the support assembly 16 preferably further includes a shaft support 106 and an end cap 32. The end cap hub 108 is fastened to the mounting structure 18. The shaft support 106 is preferably axially positioned between the drive end 74 and the rotor 22. Additionally, the preferred end cap hub 108 is integrally formed as part of the end cap 32, but in some aspects of the present invention, non-integrated securing may also be permitted.

As will be discussed in more detail below, the mounting structure 18 preferably includes a pair of plates or branches Shelves 110 and 112 support the support assembly 16. The shaft support 106 is preferably secured to the plate 110 by a plurality of shaft support fasteners 114, and the end cover hub 108 is secured to the panel 112 by a plurality of end closure fasteners 116. However, alternative fixed components are permissible without departing from some aspects of the present invention.

As best shown in Figures 18 and 19, the drive end bearing 66 is preferably mounted to The shaft support 106 is preferably mounted within the end cap 32. The drive end bearing 66 and the opposite end bearing 72 are preferably for rotationally supporting the shaft member relative to the shaft support 106 (which is fixed to the plate 112) and the end cover 32 (which is fixed to the plate 110).

The shaft support 106 preferably includes a shaft support flange that extends radially inwardly 118, which overlies a portion of the drive end bearing 66 to prevent substantial axial displacement of the drive end bearing 66 in the direction of the drive end 74, while the retaining ring 90 provides resistance to displacement in the direction of the opposite end 76.

As previously indicated, the opposed end 76 preferably has a middle section than the shaft member 64. 80 small diameter. The opposed end bearing 72 also preferably has a smaller bore 88 than the other bearings 66, 68 and 70. The bore 88 of the opposed end bearing 72 is sized such that the opposed end bearing 72 fits over the opposite end 76 but does not fit over the intermediate section 80 of the shaft member 64. More specifically, as shown in FIG. 18, the shaft member 64 includes a shoulder 120 defined between the opposing end 76 and the intermediate section 80. The movement of the opposite end bearing 72 in the direction of the drive end 74 is thus prevented by the shoulder 120.

The end cap hub 108 preferably includes an end cap hub flange 122 that extends radially inwardly, It overhangs a portion of the opposite end bearing 72. Additionally, the support assembly 16 preferably includes a spring washer 124 positioned between the opposed end bearing 72 and the end cap hub flange 122. Spring washer 124 and end cap hub flange 122 act to prevent significant axial movement of opposing end bearing 72 in the direction of opposing end 76. Although spring washers are preferred, other forms can be provided depending on some aspects of the present creation. Spring.

Rotor hub 36 preferably includes at least substantially defining the boundaries of shaft member 64 and presenting The end face 128 and the spacer 126 of the opposite end face 130 are driven. The hub bearing 68 is preferably mounted adjacent the drive end face 128 within the rotor hub 36, and the one-way bearing 70 is preferably mounted adjacent the opposing end face 130 within the rotor hub 36. Bearings 68 and 70 are used to support rotor 22 on shaft member 64 in a rotational manner, wherein one-way bearing 68 also provides selective drive interconnection between rotor 22 and shaft member 64, as will be described.

In a preferred embodiment, each of the bearings 66, 68, 72 is A ball bearing includes a respective collection of bearing balls 132, 134, and 136. However, according to some aspects of the present invention, other bearing types such as needle bearings, sleeve bearings and/or self-aligning bearings are permissible.

Preferably, as shown in FIG. 18, the bearing ball 136 of the opposite end bearing 72 is shown. The bearing balls 132 of the bearing end bearing 66 and the bearing balls 134 of the hub bearing 68 are respectively larger. More specifically, in the preferred embodiment illustrated, the bearing balls 132, 134, and 136 are sized such that the bearings 66, 68, and 72 have at least substantially equal outer diameters, but the opposed end bearings 72 The inner diameter is smaller than the inner diameter of the bearings 66 and 68.

Preferably, the outer casings of bearings 66, 68 and 72 and bearing balls 132, 134 And 136 consists essentially of steel, but the use of other materials is within the scope of this creation.

In a preferred embodiment, the one-way bearing 70 functions as both a one-way clutch and a load assembly such that it is not necessary to include a separate support bearing adjacent the one-way bearing 70. Optimally, the one-way bearing 70 is a sprag clutch bearing, such as Boca Bearing ^TM CSK203PP. As shown in FIG. 18, the one-way bearing 70 includes, in its preferred embodiment, a plurality of diagonal braces 138 and bearing balls 140 that are retained between the inner race 142 and the outer race 144. Preferably, inner race 142 and outer race 144 share the axis of rotation of shaft member 64 and rotor 22.

20 and 21 schematically illustrate the unidirectional bearing 70 in its preferred slanting clutch Radial cross section in the configuration of the device. A plurality of diagonal braces 138 are shown positioned between the inner race 142 and the outer race 144. As will be understood by those of ordinary skill in the art, the braces 138 are typically located in a cage (not shown) and can be spring loaded (also not shown) such that the braces are oriented toward a desired location for a particular application. Biased.

Figure 20 illustrates the locking configuration in which the inner race 142 is in a counterclockwise direction (below Rotation about the forward direction of Figures 20 and 21 causes torque to be transmitted from the inner race 142 to the outer race 144 via the braces 138 such that the outer race 144 rotates forward with the inner race 142. Conversely, rotation of the outer race 144 in a clockwise direction (hereinafter referred to as rearward with respect to FIGS. 20 and 21) transmits torque from the outer race 144 to the inner race 142 via the braces 138 such that the inner race 142 Rotate backwards with the outer race 144.

More specifically, the inner race 142 presents an inner race contact surface 146, and The outer race 144 presents an outer race contact surface 148. Each bracing 138 presents an inner bracing contact surface 150, an outer bracing contact surface 152, and an individual rotational or tilting axis extending therethrough that is preferably parallel to the axis of rotation of the shaft member 64. Due to the interaction shape of the contact surfaces 146, 150 and 148, 152, the inner race 142 is rotated forward (or the outer race 144 is rotated rearward) causing the braces 138 to tilt or rotate rearward (clockwise), thus increasing its diameter A radial force is created between the height and the respective bracing contact surfaces 150, 152 and the race contact surfaces 146, 148 to effectively compress or lock the inner race 142 and the outer race 144 to the braces 138 via friction. (and therefore locked each other). The inner race 142 and the outer race 144 thus rotate generally about the axis of the shaft member 64.

Moreover, as is also apparent from FIG. 20, the compression or locking action of the braces 138 generally prevents forward (counterclockwise) rotation of the inner race 142 relative to the outer race 144. From an alternative perspective, the rearward (clockwise) rotation of the outer race 144 relative to the inner race 142 is substantially prevented. For example, within reasonable tolerances, the outer race 144 cannot rotate forward more slowly than the inner race 142, or the outer race 144 cannot remain stationary or rearward as the inner race 142 rotates forward. Additionally, the outer race 144 cannot be rotated rearward as the inner race 142 remains stationary. Similarly, within a reasonable tolerance, the inner race 142 cannot rotate rearwardly slower than the outer race 144, or the inner race 142 cannot remain stationary or rotate forward as the outer race 144 rotates rearward. Still further, the inner race 142 cannot rotate forward when the outer race 144 remains stationary.

In contrast, FIG. 21 illustrates an unlocking configuration in which a rearward (clockwise) rotation of the inner race 142 relative to the outer race 144 does not substantially cause torque to be transmitted from the inner race 142 to the outer race 144 via the braces 138. . From an alternative perspective, the forward (counterclockwise) rotation of the outer race 144 relative to the inner race 142 does not substantially cause torque to be transmitted from the outer race 144 to the inner race 142 via the braces 138. That is, the torque transmission is substantially prevented such that the inner race 142 and the outer race 144 need not rotate uniformly about the axis of the shaft member 64, respectively.

More specifically, due to the interacting shape of the contact surfaces 146, 150 and 148, 152, the inner race 142 is rotated rearward relative to the outer race 144 (or equivalently, the outer race 144 is relative to the inner race 142 Rotation) causes the braces 138 to tilt or rotate forward (counterclockwise), thereby reducing their radial height and at least substantially eliminating the radial direction between the bracing contact surfaces 150, 152 and the race contact surfaces 146, 148, respectively. The force is such that the inner race 142 and the outer race 144 and the braces 138 are substantially released relative to one another. The inner race 142 and the outer race 144 are thus free to rotate generally relative to each other about the axis of the shaft member 64.

Therefore, when the outer race 144 rotates faster in the front direction than the inner race 142 At this time, substantially no torque is transmitted between the inner race 142 and the outer race 144, and when the outer race 144 is rotated in the forward direction and the inner race 142 is stationary or rearward, substantially no torque is transmitted. Similarly, when the inner race 142 is rotated faster in the rearward direction than the outer race 144, substantially no torque is transmitted between the inner race 142 and the outer race 144, when the inner race 142 is rotated in the rearward direction and the outer seat When the ring 144 is stationary or rotating forward (as previously mentioned), substantially no torque is transmitted.

In a preferred embodiment, the support assembly 16 further includes a shaft key 154 And rotor key 156. The shaft key 154 preferably securely interconnects the shaft member 64 with the inner race 142 such that the shaft member 64 and the inner race 142 rotate substantially simultaneously. Similarly, the rotor key 156 preferably securely interconnects the outer race 144 with the rotor 22 such that the outer race 144 rotates substantially simultaneously with the rotor 22. Thus, the operation of the one-way bearing 70 as described in detail above affects not only the rotation of the inner race 142 and the outer race 144, but also the rotation of the shaft member 64 and the rotor 22.

More specifically, as best shown in Figures 16 and 18, the shaft recess 158 Formed in the shaft member 64. As best shown in Figures 16, 18, 20 and 21, inner race recess 160 is formed in inner race 142. The shaft key 154 is retained in the shaft recess 158 and the inner race recess 160 in a cooperative manner.

Moreover, as best shown in Figures 13, 14, and 18, the hub recess 162 Formed in the hub spacer 126. As best shown in Figures 16-21 and other figures, outer race recess 164 is formed in outer race 144. The rotor key 156 is retained in a cooperative manner in the hub recess 162 and the outer race recess 164.

However, as an alternative to or in addition to the keys 154 and 156, permission may be permitted Set up an alternate interconnect. For example, an adhesive, a weld or a press fit can be used, or a latch and/or a peg can be provided.

In view of the operation of the one-way bearing 70 and the inner race 142 and the outer race 144 to The above-described detailed description of both the interconnection of the shaft member 64 and the rotor 22 will be readily apparent to those of ordinary skill in the art, and can be directed to the configuration of the one-way bearing 70 and its shaft member. A number of general statements are made regarding the effects of 64 and rotor 22. For example, in a preferred embodiment, the one-way bearing 70 is configured such that when the shaft member 64 rotates in the first direction and the rotor 22 does not rotate relative to the shaft member in the first direction (That is, when the rotor 22 does not rotate faster than the shaft member 64 in the first direction), the shaft member 64 generally transmits torque to the rotor 22. In a preferred exercise bicycle embodiment, for example, when the shaft member 64 is rotated forward by the user's pedal, the shaft will generally drive the rotor 22, which is also at least substantially equal to the rotational speed of the shaft member. Spin in the front direction.

The one-way bearing 70 is also preferably configured such that when the shaft member 64 is in the first direction In the opposite direction of rotation in the second direction, the shaft member 64 is substantially prevented from transmitting torque to the rotor 22. Considering again the preferred embodiment of the exercise bike, the shaft member does not substantially transmit torque to the rotor 22 when the shaft member 64 is rotated rearwardly by the user stepping back. For example, the forward spinning rotor 22 will be substantially free to continue to rotate forward.

The one-way bearing 70 is also preferably configured such that when the two components are in the first direction Rotating, while the rotor 22 is generally rotated faster than the shaft member 64, generally prevents the shaft member 64 from transmitting torque to the rotor 22 (i.e., the rotor 22 is "freewheel"). Continuing with the exercise bicycle similar example, if the pedal is quickly stepped in, for example, a few seconds, then the pedaling rate is slowed down so that both the shaft member 64 and the rotor 22 rotate forward but the rotor 22 advances faster than the shaft member 64. When rotating, the rotor 22 is empty. Transfer can appear. Once the rotor 22 has been slowed down to substantially the same speed as the shaft member 64 due to friction and other forces, the shaft member 64 will then drive the rotor 22 again.

Still further, the one-way bearing is preferably configured such that the shaft member 64 is substantially prevented For the rotation of the rotor 22 in the first direction. In a similar example of a fitness bike, for example, the rotor 22 is generally prevented from rotating forward slightly slower than the forwardly moving pedal, assuming that the pedal is directly interconnected with the shaft member (so that one revolution of the pedal causes one rotation of the shaft member) . Similarly, the rotor 22 is substantially unable to rest or rotate backward as the pedal moves forward. Similarly, if the rotor 22 spins backwards, the pedal is generally unable to spin forward, remain stationary, or even spin backwards slower than the rotor 22.

As will be readily apparent to those skilled in the art, it can also be from the center of the rotor. The angle presents the above situation. For example, the one-way bearing 70 is configured such that when the rotor 22 rotates in the second direction and the shaft 64 does not rotate in the second direction relative to the rotor 22, the rotor 22 transmits torque to the shaft 64. The one-way bearing 70 is also configured such that when the rotor 22 is rotated in the first direction, the rotor 22 is prevented from transmitting torque to the shaft 64. Still further, the one-way bearing 70 is configured such that when both the rotor 22 and the shaft 64 rotate in the second direction but the shaft 64 rotates faster than the rotor 22, the rotor 22 is prevented from transmitting torque to the shaft 64.

In a preferred embodiment, the support assembly 16 is as described above The assembly is configured such that the support assembly 16 can be assembled by hand. For example, bearing bores 82, 84, 86, and 88 are preferably sized for sliding fit relative to the associated position of shaft member 64. However, it is possible to permit the use of press fit or other fits that are not advantageous for manual assembly in alternative embodiments.

In addition, the support assembly 16 can preferably be blindly combined. However, genus may be permitted Modifications within the scope of this creation will result in blind combinations becoming impossible.

Mounting structure

As discussed in more detail below and as best shown in FIGS. 1 and 2, the mounting structure 18 preferably includes a base 166 that is configured for attachment to the appliance 10. Mounting structure 18 also preferably includes a pair of at least substantially radially extending plates or brackets 110 and 112, which are secured to base 166. The panels 110 and 112 preferably at least partially define a machine storage space 168 therebetween, wherein the machine 14 is mounted to the panels 110 and 112 for at least partial positioning in the machine storage space 168. More specifically, the plates 110 and 112 are preferably at least partially extended adjacent to each of the previously described axial machine edges 26 and 28, and the base 166 is preferably positioned at least substantially radially at the outermost circumference. The machine surface 24 is external. That is, the machine 14 is supported in a cantilever manner relative to the base 166.

Preferably, the machine 14 is mounted relative to the panels 110 and 112 such that the respective gaps or spaces 170 and 172 defined between the panels 110 and 112 are at least substantially similar to the axial edges 26 and 28 of the machine 14. That is, machine 14 is preferably substantially centered between plates 110 and 112.

It will be understood by those skilled in the art that it is customary to use spacers between the opposing circumferential surfaces of the rotor of a given machine and the stator to orient the rotor and stator relative to one another during manufacture, assembly and/or installation. Positioning. For example, for an external rotor motor, a shim can be placed between the outer face of the stator and the adjacent inner face of the rotor. However, the fabrication, assembly, and installation of the authoring machine 14 is achieved without the use of spacers, at least in part due to the advantages provided by the pedestal 166 design described in detail below. However, depending on some aspects of the present creation, the use of a gasket may be permitted.

Preferably, the base 166 is cast or molded. More specifically, the pedestal 166 is more Good contains die-cast metal. However, in accordance with some aspects of the present invention, it may be permitted to form the pedestal in an alternative manner. For example, the pedestal can be formed from a combination of casting and molding, and/or can be formed, in whole or in part, by machining. In addition, the base may alternatively comprise a different material, such as plastic.

In a preferred embodiment, best illustrated by Figures 3 through 10, the base 166 A pair of axially spaced apart at least substantially parallel sides 174 and 176 are present, and a split draft face extending between the sides 174 and 176 and interconnecting the sides. The split draft face 178 will be discussed in greater detail below.

The base 166 preferably further presents opposite the split draft face 178 and is lateral A bottom surface 180 of the sides is extended and interconnected between 174 and 176. The bottom surface 180 is preferably at least substantially perpendicular to the sides 174 and 176.

In a preferred embodiment, the base 166 includes a base flange 182, which The base flange is configured for connection to the appliance 10. The base flange 182 preferably includes a pair of base flange sections 184 and 186, each of which projects axially beyond the counterpart of the sides 174 and 176, and each of which includes for attachment A plurality of base fastener receiving grooves 188 are attached to the base fasteners (not shown) of the appliance 10.

The split draft face 178 preferably includes a first portion 190 adjacent the side 174 and a second portion 192 adjacent the side 176. The split draft face 178 also preferably includes a front region 194 and a rear region 196. As best shown in Figures 7 and 8, first portion 190 and second portion 192 are preferably angled relative to one another and adjacent along a draft line or parting line 198, respectively. More specifically, the first portion 190 and the second portion 192 are each preferably angled away from the draft line 198 toward the bottom surface 180. In a preferred embodiment, this configuration facilitates easy removal of the base 166 from the mold.

The draft or parting line 198 is preferably at least substantially identical to the sides 174 and 176. The distance is such that the first portion 190 and the second portion 192 have at least substantially the same width. Additionally, the draft line 198 is preferably straight. However, according to some aspects of the present invention, offset, bend, step and/or zigzag draft lines may be permitted.

In a preferred embodiment, the first portion 190 of the split draft face 178 The second portion 192 preferably defines the concave curved region 200 of the pedestal 166 in a cooperative manner. As best shown in Figures 1, 2 and 19, the curved region 200 and the outermost circumferential machine surface 24 previously described are preferably at least substantially concentric. In a preferred embodiment, therefore, a substantially constant radial gap 202 is maintained between the base 166 and the machine 14 regardless of the rotational position of the rotor 22.

As best shown in Figures 3 and 4, in a preferred embodiment, the side Each of the faces 174 and 176 preferably presents at least substantially flat abutment regions 204 or 206, respectively. Moreover, as best shown in FIG. 19, each of the brackets or plates 110, 112 preferably presents respective at least substantially flat axial interior faces 208 or 210. One portion of each axial inner face 208 or 210 is preferably abutting a respective one of the abutment regions 204 or 206 such that the abutment regions 204 and 206 are at least substantially parallel to the inner faces 208 and 210.

The laying of the draft line 198 on the split draft face 178 enables casting or The at least substantially flat abutment regions 204 and 206 are molded and formed without mechanical machining, thereby reducing manufacturing costs associated with the pedestal 166. Preferably, the entire base 166 is formed without machining, but in accordance with some aspects of the present invention, machining of the abutment region and/or other portions of the base may be permitted.

In a preferred embodiment, the base 166 defines a plurality of connection locations 212, comprising a plurality of fastener receiving holes 214. The boards 110 and 112 preferably define a corresponding plurality of boards Hole 216. Preferably, the plates 110 and 112 are fastened to the base 166 using discrete plate fasteners 218 that extend through corresponding ones of the plate apertures 216 into the corresponding one of the fastener receiving apertures 214 in the base 166 such that the interior of the panel Faces 208 and 210 are contiguous with adjacent regions 204 and 206 of sides 174 and 176 in the manner described above.

More specifically, as shown in FIG. 3, FIG. 4 and other figures, the fastener receiving hole The first set 214a of 214 is preferably defined in the first side 174, and the second set 214b of fastener receiving apertures is defined in the second side 176. Similarly, a first group 216a of plate holes 216 is preferably formed in the first plate 110 and a second group 216b of plate holes 216 is formed in the second plate 112.

As shown in Figures 9 and 10, the fastener receiving aperture 214 is preferably a blind aperture. also That is, the fastener receiving holes preferably do not extend through the entire base 166.

Preferably, the plate aperture 216 is sized such that only the panel fastener 218 is provided small Void. This small gap facilitates the preferred shimless motor configuration briefly described above. However, depending on some aspects of the present creation, larger voids may be permitted.

Although the fastening configuration described above is preferred, the plate is fastened to the base Alternative components fall within the scope of some aspects of this creation. For example, the panel fasteners may not be discrete, but in the form of pegs extending from the panel, or the components may be fastened to each other using a latch and/or an adhesive. It is also permissible to provide a through hole in the base.

The motor or generator assembly 12 preferably exhibits at least in part due to the above A good component parallel and vertical relationship is described in detail for the advantages provided by the preferred pedestal 166. For example, those of ordinary skill in the art will appreciate that the base 166 is stable and substantially solid, which has been determined to significantly reduce the warpage of the plates 110 and 112 and when the machine 14 is mounted relative to the plates 110 and 112. Irregularities caused.

Still further, the pedestal 166 preferably establishes a reference plane (eg, by the pedestal 166) The bottom surface 180 is defined), wherein other components of the machine can be positioned according to the reference plane. For example, the shaft member 64 is preferably positioned such that its centerline extends generally parallel to the plane defined by the bottom surface 180.

The preferred forms of the present invention described above are for illustrative purposes only and should not be used in a limiting sense to interpret the scope of the present invention. As apparent from the above, the obvious modifications of the exemplary embodiments can be readily made by those skilled in the art without departing from the spirit of the present invention.

The creator hereby declares that it intends to determine the rather reasonable scope of the creation based on the principle of equality, without departing from the scope of the text of the creation as set forth in the scope of the patent application below. Evaluate for any device.

10‧‧‧ Appliances

12‧‧‧Motor or generator assembly

14‧‧‧Motor or generator assembly

16‧‧‧Support assembly

18‧‧‧Installation structure

20‧‧‧ Stator

20a‧‧ core

20b‧‧‧Wiring

22‧‧‧Rotor

24‧‧‧ outermost machine surface

26‧‧‧Axial machine edge

30‧‧‧Leader

32‧‧‧End cover

36‧‧·wheels

40‧‧‧Inertial ring

110‧‧‧ board/bracket

112‧‧‧ board/bracket

166‧‧‧Base

168‧‧‧machine storage space

170‧‧‧ gap or space

174‧‧‧ side

176‧‧‧ side

178‧‧‧ split draft face

182‧‧‧Base flange

184‧‧‧Base flange section

188‧‧‧Base fastener storage slot

190‧‧‧Part 1

192‧‧‧Part II

194‧‧‧ front area

200‧‧‧ concave curved area

202‧‧‧ radial clearance

210‧‧‧Axial internal surface

216‧‧‧ plate hole

216a‧‧‧The first group of plate holes

218‧‧‧ board fasteners

Claims (20)

A motor or generator assembly for use with an appliance, the motor or generator assembly comprising: a motor or generator comprising: a rotor rotatable about an axis, and a stator, the machine exhibiting an axis To the extended radially outermost circumferential surface, the machine presents a pair of axially spaced apart axial edges, each of the axial edges extending generally radially inward from the circumferential surface; and a mounting structure, Supporting the machine on the appliance, the mounting structure comprising - a pair of at least substantially radially extending plates, the plates at least partially defining a machine receiving space therebetween, the machine being mounted to the brackets, So as to be at least partially positioned in the machine storage space, the plates extend at least partially adjacent to each of the axial edges, and a base that is at least substantially radially positioned at the machine Outside the circumferential surface, the base is configured for attachment to the appliance, the base exhibiting a pair of axially spaced sides, wherein each of the plates abuts one of the sides Fastened by individual. The motor or generator assembly of claim 1, wherein the base is a cast or molded pedestal that extends between the sides and interconnects one of the sides to split the die face, The split drafting surface includes a first portion adjacent to one of the one of the sides and adjacent to the first A second portion of one of the second sides, the first portion and the second portion being angled relative to each other, the first portion abutting the second portion along a draft line. The motor or generator assembly of claim 2, the base further exhibiting a bottom surface that faces the split die and extends between the sides and interconnects the sides. The motor or generator assembly of claim 2, wherein the draft line is at least substantially equidistant from the first one of the sides and the second one of the sides, the draft The line is straight. The motor or generator assembly of claim 2, the split draft face includes a curved region that is recessed about the axis of rotation. In the motor or generator assembly of claim 5, the curved region and the outermost circumferential surface are at least substantially concentric. The motor or generator assembly of claim 5, the split drafting surface further comprising a front region and a rear region, the curved region extending between the front region and the rear region and interconnecting the regions . A motor or generator assembly as claimed in claim 2, the base comprising a die cast metal. A motor or generator assembly of claim 1, wherein each of the sides presents an at least substantially flat abutment region, Each of the plates presents an at least substantially flat axial inner face, one of the portions of each of the axial inner faces abutting one of the adjacent regions. In the motor or generator assembly of claim 9, the adjacent regions are at least substantially parallel to the interior systems. Such as the motor or generator assembly of claim 9 of the patent scope, the adjacent regions are formed without machining. A motor or generator assembly of claim 1, wherein each of the axial edges of the machine and a neighbor of the plates define a space therebetween, wherein the spaces are substantially akin. A motor or generator assembly as claimed in claim 1 which lacks a gasket. A motor or generator assembly as claimed in claim 1 wherein the rotor at least partially defines a boundary of the stator, the rotor defining the circumferential surface. A motor or generator assembly as claimed in claim 1 wherein the base includes a flange configured to be coupled to the appliance. A motor or generator assembly of claim 15 wherein the flange includes a pair of flange segments, each of the flange segments projecting axially beyond one of the sides . The motor or generator assembly of claim 1, wherein the base defines a plurality of attachment locations at which the panels are fastened to the base. The motor or generator assembly of claim 17, wherein the connection position comprises a plurality of fastener receiving holes, the mounting structure further comprising a plurality of fasteners extending to corresponding ones of the fastener receiving holes In order to fasten the boards. The motor or generator assembly of claim 18, the plurality of fastener receiving holes including a first set of fastener receiving holes defined in one of the first sides and defined in the first a second set of one of the fastener receiving apertures in one of the sides. The motor or generator assembly of claim 18, wherein the plates define a plurality of plate holes corresponding to the fastener receiving holes, the fasteners extending through the plate holes to fasten the plates .